Hydraulic pump for use in the bottom of wells



J. PENROD Feb. 16, 1932.

HYDRAULIC PUMP FOR USE IN THE BOTTOM OF WELLS 5 Sheets-Sheet 1 Filed May 15 1926 Feb. 16, 1932. J. PENROD 1,845,179

HYDRAULIC PUMP FOR USE IN THE BOTTOM OF WELLS Filed May 13, 1926 5 Sheets-Sheet 2 r 4 180 k 161 I V 3mm kw T Jfl/YENRQD;

107 $1 109 z 5 ZIO 10 60 105 flbtozmq F iled May 13. 1926 5 Sheets-Sheet 3 /////VVI J. PENROD HYDRAULIC PUMP FOR USE IN THE BOTTOM OF WELLS Filed May-l3 1926 5 Sheets-Sheet 4 Feb. 16, 1932 Feb. 16,1932. J. PENROD HYDRAULIC PUMP FOR USE IN THE BOTTOM OF WELLS Filed May 13, 1926 5 Sheets-Sheet 5 Patented :Feb. 16, 1932 UNITED STATES PATENT OFFICE JOHN PENROD, OF OKMULGEE, OKLAHOMA, ASSIGNOR OF ONE-HALF TO ROBERT D. THOMPSON, F OKMULGEE, OKLAHOMA HYDRAULIC PUMP FOR USE IN THE BOTTOM OI WELLS Application filed May 13, 1920. Serial No. 108,880.

This invention relates to hydraulic pumps especially adapted for use .in the bottom of oil and other wells.

I am aware that centrifugally operated pumps with a power unit such as an electric motor have been employed in the bottoms of wells, but such pumps must of necessity come in direct contact with the fluid to be elevated, with the result that sand suspended in the fluid wears away the blades and other parts of the pump so that the results obtained are not entirely satisfactory.

, The pump most in vogue is, as is well known, located at the lower portion of the well and is reciprocated by rods which extend from a power unit on the surface so that the power unit must not only lift the weight of the fluid, but also must lift the rods, which in an oil well of average depth may range around 4000 or 5000 pounds. The presence of sand in the fluid makes it necessary to pull the pumping equipment at the lower end of the rod so that pumping is frequently interrupted. In addition to this, the present equipment is more or less costly to maintain as compared with the value of the production, especially when the production is settled and somewhat small, for the reason that one or more attendants must remain on a lease and take care of the equipment of the various wells thereon, all of which increases the cost of production and therefore reduces the net income from the operation.

It is, therefore, an important object of this invention to provide a pump adapted to be placed in the bottom of a well and having a self-contained power unit which sets up an effective hydraulic pressure which may be employed in the reciprocation of a main elevating pump, the products of the well being at all times spaced from the hydraulic power unit so that sand which may be present in the products of the well will not have a destructive effect on the hydraulic power unit.

A further and equally important object of the invention is to provide a hydraulically operated pump which is automatically set in operation when the level or pressure of the fluid in the well exceeds a predetermined height whereby the necessity of employing an attendant to start and stop the well at intervals is overcome.

Another feature of the invention is to provide a hydraulically operated pump which by reason of having a self-contained power unit or prime mover will avoid the necessity of employing rods so troublesome in connection with present equipment.

Other objects and advantages will be apparent during the course of the following 00 description In the accompanying drawings forming a part of this application and in which like numerals are employed to designate like parts throughout the same,

Figure 1 is a vertical sectional view through the main pump by means of which the fluid is elevated, the ump shown in this figure being reciprocated a hydraulic power unit having a body of uid entirely separted from the products of the well.

Figure 2 is a vertical sectional view through a valve mechanism by means of which the non-compressible fluid under pressure is supplied alternately to opposite sides of the mov- 7;, able piston connected to the pump plunger shown in Figure 1 whereby the main pump plunger is reciprocated, the view being taken on line 22 of Figure 9.

Figure 3 is a vertical sectional view illustrating a pump by means of which a hydraulic pressure is set up for the operation of the piston shown in Figure 1.

Figure 4 is a detail sectional view illustrating a prime mover embodied in the invention.

Figure 5 is a horizontal sectional view taken on line 5-5 of Figure 2.

Figure 6 is a horizontal sectional view taken on line 6-6 of Figure 2.

Figure 7 is a horizontal sectional view taken on line 7-7 of Figure 1.

Figure 8 is a horizontal sectional view taken on line 88 of Figure 2.

Figure 9 is a horizontal sectional view taken on line 9-9 of Figure 2. I

Figure 10 is a horizontal sectional view taken on line 1010 of Figure 3.

Figure 11 is a vertical detail sectional view taken on line 11'11 of Figure 3.

Figure 13 is a vertical sectional view- 6 through a valve casing embodied in the invention.

Figure 14 is a side elevation of a rotary valve embodied in the invention and adapted to be received in the valve casing shown in Figure 13.

Figure 15 is a fragmentary vertical sectional View through the improved pump.

Figure 16 is a sectional View through a switch embodied in the'invention.

Figure 17 is a longitudinal section through the complete apparatus showing the parts diagrammatically. Y i

In the drawings, the numeral 10 designates a motor casing, the lower end of which is provided with a bushing 11 receiving a bearing member 12 of the armature shaft 13 of an electric motor. Figure 4 plainly illustrates that the lower portion of the armature shaft 13 is provided with an annular shoulder 14Which rests upon a series of antifriction elements 16 and the anti-friction ele-' ments are in turn mounted on a support 17. The bushing 11 is hollow and receives a quane tity of oil by means of which the anti-friction elements 16 and a bearing 20 are lubricated to permit the turning of the armature shaft 13 with a minimum of resistance. The

.casing 10 encloses a suitable electric motor or a series of motors of appropriate power to operate the hydraulic pump to be described.

Particular attention is directed to the fact that the electric motor is at the extreme bottom of the well and is submerged in the fluid so that heat generated by the motor will be effectively taken up by the products of the well. In this connection it will be noted that the shell 10 is thin enough to allow for the effective transmission of the heat and is at the same time stout enough to withstand the pressure to which the same will be subjected.

In carrying out the invention a feed line 24 is extended in through the casing 10 and has connection in the usual and well-known manner with the electric motor. The feed line 24 extends from a suitable source of electric energy at the surface and a switch is provided on the surface so that the supply of current to the motor may be controlled at will.

The upper portion of the casing 10 has threaded connection with a bushing 40 which rotatably receives a head 41. Figure 4 plainly illustrates that the head 41 is provided with a squared socket for the reception of the squared upper end of the armature shaft whereby a driving connection is established between the armature shaft and the head.

' The upper portion ofthe head is provided with a beveled surface against which a ring 42 is engaged and'the outer side of the ring is provided with a suitable piston rmg 43 by for the reception of springs 46 which bear down on the ring 42 and thereby urge the ring into liquid-tight contact with the head.

he arrangement described provides an ab solutely fluid-tight joint between the electric motor casing and a low pressure reservoir immediately above, which low pressure reservoir is defined by a tubular member 47. Suitable anti-friction means 49 permit of the rotation of the head 41 with a minimum of friction.

To further effect a liquid seal between the head 41 and the fixed parts such as the bushing 40, the lower portion of the bushing is provided with a ri g 50 urged into engagement with the adjacent portion of the head 41 by suitable springs as shown in the drawmgs.

The head '41 has rigid connection with the lower end of a combined fluid conductor and power transmitting shaft 55 which as shown in Figure 3 extends through the low pressure cham er. The lower portion of the combined fluid conductor and power transmitting shaft is provided with apertures for the passage of the fluid under a low pressure so that the fluid may pass upwardly through the member 55 and into what might be said to be a centrally arranged manifold 56 of a hydraulic pump consisting of a number of cylinders 57. Figure 3 plainly illustrates that the block 58 having the cylinders 57 is rigidly mounted on the combined fluid conductor and power transmitting shaft 55 to turn therewith and that the pistons in the cylinders when reciprocated will bring about the pumping of the fluid from the manifold into a combined fluid conductor and power transmitting shaft 60. I

More specifically, communication vbetween the manifold 56 andthe cylinders 57 is controlled by ball valves 62 so that when the pistons move downwardly the balls are elevated and fluid is drawn in from the manifold to the cylinders. It is believed to be plain from from Figure v3 that when the pistons are moved upwardly a series of ball valves 64 are unseated against the pressure of springs 66 so that the fluid is positively directed into the combined fluid conductor and power transmitting shaft designated by the numeral 60. 1

The pistons have connection with rods 70 universally connected as indicated at 71 to an actuating member 7 2; The actuating member is in turn received in a continuous cam slot 73 in a cam member 74 fixed in any suitable manner upon the upstanding portion 75 of a spider 76. The spider, in addition to functioning as a support for the cam, also ICC acts to connect the member 47 and the tubular casing 7 8 immediately above.

In the operation of the improved hydraulic pump the shaft 55 is turned and the cylinder block 58 is also turned, with the result that the actuating member 7 2 is turned in the cam slot 73 to bring about the reciprocation of the pistons in their proper order. A guide plate 80 is rigidly mounted on the upper portion of the mem er 55 and is provided with gpenings to receive and guide the piston rods In summarizing the 0 eration of the invention as thus far described, it will be seen that when the electric motor is energized the shaft 55 will be set in motion and that the pistons in the cylinders 57 will reciprocate to bring about the movement of the fluid from the low pressure chamber through the combined fluid conductor and power transmitting shaft 60. However, it is preferable to relieve the electric motor of the weight of the column of fluid above and the major pumping load until it has attained sufiicient momentum to carry the load without laboring, and I therefore provide an automatic means whereby the operation of the shaft 60 below a predetermined speed results in returning the fluid to the low pressure chamber without acting on the main fluid pump.

In describing this feature of the invention attention is invited to Figure 3 which illustrates that the lower attaching member 85 of a centrifugal governor is anchored to the shaft 60 and that the upper ring 86 is movably mounted on the shaft 60. The springs 7 7 of the centrifugal governor are normally held in the position illustrated in Figure 3 and when the shaft 60 makes a predetermined number of revolutions per minute, the balls 90 are moved outwardly so as to draw the ring 86 downwardly.

Referring now to Figure 11, it will be seen that a valve stem 91 is connected to the upper movable ring 86 of the governor and moves through a valve casing 92. When the governor is operating at a slow speed the ring 86 is, of course, in a non-operative position, but when the speed of the governor exceeds a predetermined point, the ring 86 is moved downwardly so that the stem 91 is caused to move across the passage in the valve 93 to close the same. Figure 11 plainly illustrates that the valve 93 is threaded into the fluid container 60 and has an opening communicating therewith.

In the operation of this part of the invention, when the motor exceeds a predetermined number of revolutions per minute the ring 86 is moved downwardly and the stem 91 will also descend so that it extends across and closes the opening in the valve casing 93, whereupon the escape of the fluid through the valve 93 is prevented. However, when the governor is operating below a predeterby the pump shown in Figure 3 is preferably free 0 likely to wear the pump rapidly and cause theall solid particles which would be frequent withdrawal of the same to the surface. In other words, the fluid directly acted on by the pump shown in Figure 3 is completely separated and sealed off from the natural products of the well so that by no chance may the natural products of the well, such as sandy fluid, come into destructive contact with those parts so essential to the continued operation of the well and so susceptible to damage as a result of contact with sand.

When the motor attains a predetermined number of revolutions per minute the fluid travels up under a high pressure through the fluid conductor andpower transmitting shaft 60 past the valve 93 and enters a conductor 60' and then enters a high pressure chamber 95. From the high pressure chamber 95 the fluid is distributed to alternately act on opposite sides of a main fluid elevating piston 96 shown in Figure 1.

The fluid which passes up through the member 60 as clearly shown in Figure 2 is distributed by a rotary valve 100 operating within a fixed valve casing 101. The speed of the rotary valve 100 is much lower than the speed of the member 60 and'this reduction in speedis accomplished by a speed change devigce clearly shown at the bottom of Figure The speed change device consists of a pair of spaced plates 103 which carry the gears 104 and 105. The upper portion of the conductor 60 is connected to the lower portion of the pipe 60 by a coupling member 106, the outer portion of which is provided with an annular series of gear teeth in constant engagement with a spur gear 107 forming a part of the member 105. Immediately below the gear 107 the member is provided with an annular series of gear teeth 108 in constant mesh with a rotatable ring gear 109. The ring'gear 109 is in mesh with a combination gear 110, the upper portion of which is provided with gear teeth engaging theinternal teeth of a gear 112. The arrangement described and illustrated brings about the turning of the member 112 sub-' threaded into the ring gear 112 so that the rotary valve turns at the same speed as does the gear 112.

Careful consideration of Figures 2, 6, 13

. and 14 will show that the valve casing 101 is provided with longitudinally extending fluid passages A and opening out through the upper portion thereof and in constant communication with the high pressure chamher. It will therefore be seen that the high pressure present in the chamber shown in Figure 2 will also be constantly present in the passages A and B. The turning of the valve results in the periodical registration of a port therein with an arcuate port 121 at the lower portion of the passage A. When the fluid under pressure travels down through the passage A, out through; the port 121 and into the port 120, it wi pass out of the valve 100 by a port 123 an enter combined feed and return passages 3 and 4. At this point it is. noted that the function of the passages 3 and 4 is exactly the same and I have employed two of these passages merely to provide increased capacity without a corresponding increase in the size of the parts.

In summarizing, this part of the operation of the rotary valve, it is pointed out that when the port 120 registers with the port 121, fluid may enter the rotary valve and pass out through the port 123 and enter the passages 3 and 4 by way of an arcuate port 126 as clearly shown in Figure 13. As shown in Figure 13, the arcuate port 126 extends a substantial distance about the valve casing 101 to establish constant communication between the passages 3 and 4, and during the entire period of registration of the port 123 with the port 126, fluid may pass through the rotary valve and into the passages 3 and 4. The port 120 is brought into registration with the port 121 at the same time the port 123 is brought into registration with the port 126 and the registration of these pairs of ports is broken simultaneously. The fluid under pressure which is supplied to the passages 3 and 4 flows upwardly through suitable extensions of the passages and acts on the under side of the piston 96 to elevate the same. v

The tubular extensions of the passages 3 and 4 are confined between the upper portion of the valve casing 101 and the lower portion of a head member 130. More specifically, the tubular extensions of the passages 3 and 4 are extended through a spider-like member 131 and establish communication be- The cylinder within which the piston with a shoulder 143 which'presses down ona coactin shoulder of the conductor 130. Hence it is that the member 130 is pressed down hard so that the same will exert a pressure on the extensions of the passages 3 and 4 to hold thesame in place. Figure 2 illustrates thatthe ends of the extensions of the passages 3 and 4 engage gaskets by means of which fluid-tight joints are established at the ends of the same.

At this point it is-noted that an air cushion is preferably maintained in the upper portion of the high pressure chamber, to provide for the uniform operation'of the invention.

On the descent of the piston 96 the fluid below the same is returned by way of the passages 3 and 4 and at that time, of course, the ports 120 and 123 will be closed so that the fluid passes these ports and continues its descent through the passages 3 and 4 until it enters a port clearly shown in Fi re 13. The turning of the valve brings a out the registration of an exhaust port 151 with the port 150 so that the fluid which travels downwardly through the passages 3 and 4 may enter the rotary valve and travel out through an outlet passage 153. which is discharged by way of the port 153 returns to the low pressure chamber and is again subjected to the action of the hydraulic pump so that a substantially constant hydraulic pressure is maintained.

As previously stated, the passage B in the valve casing has constant communication with the high pressure chamber and the lower portion of the passage B has constant communication with an arcuate port 160. Referring now to Figure 14, it will be seen that the rotary valve is provided with a radial port 161. The port 161 in the rotary valve has communication with an outlet port 163. Theport 163 is adapted for registration with an arcuate port 164 corresponding to the port 126 in the valve casing and the ends of the arcuate port 164 communicate with the when the port 161 registers with the port the fluid under pressure in the passage B. may flow downwardly, laterally, and then into the port 161 and out throughthe port 163. The fluid which flows out through the port 163 under the influence of the hydraulic motor previously described enters the passages 1 and 2. Attention is now directed to Figure 2 which illustrates that the fluid which passes upwardly through the passage 1, and for that matter the passage 2, travels up through tubular extensions of the passages 1 and 2 and into passages 168 in the head 130.

passages 1 and 2. Therefore,

A ters a passage 17 5, the upper end of which- The fluid which thus enters the passage 168 passes out through openings 170, and enis shown in Figure 1 as having constant communication with the. main cylinder 140 at a point above the main actuating piston 96.

Hence it is that the fluid which enters the cylinder 140 above'the piston 96 will .force t e piston 96 downwardly to bring about the return of the fluid beneath the piston.

When the piston 96 again partakes of its upward stroke, the previously eflective fluid above the piston 96 is returned by way of the passage 175 to the passages 1 and 2, and at that time the rotary valve 100 will be positioned so that port 180 therein registers with an arcuate port 181 in constant communication with the passages 1 and 2. The fluid which is thus received in the port 180 will travel down through the outlet 153 and return to the low pressure chamber for subsequent pumping purposes. 1

In summarizing the cycle of operation of the fluid which travels through the passage B,

it will be seen that when the port 161 registers with the lateral branch 160, the fluid will travel downwardly through the passage B into the rotary valve and out through the radial port 163 so thatit issupplied to the passages 1 and 2. The fluid whlch is passed through the passages 1 and 2 under pressure will be supplied by way of the passage 175 to the upper side of the plston 96 to bring about the descent of the piston. Thus, the fluid pressure constantly prevailing within the chamber 109 acts alternately on opposite ends of the piston 96 to reciprocate the same. The application of pressure alternately to opposite ends of the piston 96 is brought about by the rotary valve and the associated valve casing, both of these parts being positioned in the line of flow of the fluid under pressure from the high pressure chamber 95 to the cylinder 140.

When the port 120 of the rotary valve is in register with the arcuate .port 121 in the valve casing, the fluid under pressure is allowed to flow downwardly from the high pressure chamber through the port A the registering ports 121 and 120, out through the port 126-and up through the passages 3 and 4. The flow of fluid under pressure up through the passages 3 and 4 will result in the ascent of the piston 96. On the other hand, when the position of the rotary valve is reversed, the passage A or more specifically the port 121 thereof is closed and the descent of the piston will result in the flow of the fluid below the piston through the passages 3 and 4 and out through the passage 153 into the low pressure chamber. From the low pressure chamber the fluid is picked up by the pump shown in Figure 3 and is returned to the high pressure chamber.

Adverting now to the passage B and the asis in communication with the arcuate port- 160 the pressure fluid may enter the port 160, pass out through the port 163, travel through the arcuate port 164 and ascendthrough t e passages 1 and 2. The; fluid directed up .through the passages 1 and 2 will travel through the passage 17 5 and act on the 11 per side of the piston 96 to bring about the own stroke of the pump. On the subsequent up stroke of the piston 96, the fluidabove the same is directed down through the passage 175 andthe ports-1 and 2. At this time, the outlet means 180 and 153 are in communication with the arcuate passage 181, the latter being in communication with the passages 1 and 2 so that on the up stroke of the piston, the fluid above the same is returned to the low pressure chamber to be picked up by the pump shown in Figure 3 and return to the high pressure chamber.

The reciprocation of the main piston 96 by the means just described results in the reciprocation of a fluid pumping plunger or piston 200 as the piston has connection with the plunger through the medium of a piston rod 201.

Figure 1 plainly illustrates that the plunger 200 has a longitudinally extending socket 203 extending from the major portion thereof and receiving the upper portion'o fthe rod 201 and the plunger operates in a sleeve 204, the upper portion of which is beveled to a rather sharp edge to prevent the entrance of sand or sandy fluid into the space between the plunger and the sleeve. The particular purpose of the socket 203 is to define somewhat of a gas trap or chamber so that in the operation of the pump gas will be collected therein and prevent sand or sandy fluid from lodging between the sleeve 204 and the piston 201 and possibly working its way down into the cylinder 140. The success of the invention resides in maintaining the fluid for actuating the piston 96 entirely separate from the natural products of the well and sand therein. As the 'sleeve 204 at all times extends above the lower end of the plunger or piston 200, sand cannot easily work its way into the sleeve and into the cylinder 140. The sleeve 204 is threaded on the closed lower end 206 of the main pumping barrel 207.

Figure 1 illustrates a double acting pump adapted to receive fluid from the well by way of inlet valves 210 and 211 and the fluid is discharged from the barrel by outlet valves 212 and 214.

On the descent of the plunger or piston 200 the fluid beneath the plunger is forced out through the valve 212 and through the passage 216;" Figure 1 clearly illustrates that the upper ortion of the passage 216 extends into the tu ing 218 to bring about the movement of the fluid up through the tubing.

- The valve 214 1s located at the extreme upper end of the barrel 207 so that on the up stroke of the plunger or piston fluid will be elevated.

At this point attention is directed to tne fact that a number of the valves 214 or their equivalents may be employed as spaced points in the tubing to avoid settling of the sand at the main pump and possibly freezing same. In other words, when the pump is not in operation the presence of the spaced valves 214 at various places in the tubing prevents the sand in the fluid from settling and possibly interfering with the continued operation of the pump. In other words,.the sand, if any, which settles will be distributed throughout the length of the tubing.

The feed line designated by the numeral 24 ma be provided with lateral branches 290 which may extend into the motor housing and connect with the field coil in the usual and well-known manner. Of course. as previously stated, a master switch may be employed at the surface to control all of the motors simultaneously.

Figure 16 illustrates an automatic circuit closer adapted to be operated by the pressure of the natural fluid in the well so that when a predetermined quantity of fluid collects in the well the motors are automatically set in operation and continue to pump until the fluid drops below a' predetermined point. This renders the entire pump more or less automatic. This arrangement makes it unnecessary for an attendant to start the pump and shut the same down when the level of the fluid drops below a predetermined point. In fact, the arrangement shown in the drawings is superior to human operation of the invention as the motors will start in operation at exactly the right moment and will stop when p the level of the fluid drops below a predetermined point.

The switch shown in Figure 16 comprises have binding connection with the electric line. Of course, the end members 301 and 302 are effectively insulated from the conductors in the electric, line. The contacts 304 of one secrectly in the path of travel and are adapted to be engaged by the movable contacts 305 of the other section of the line whereby the engagement of the contacts 304 and 305 completes the electric circuit through the motors.

The movable contacts 305 are carried by a pressure responsive piston 308 having a fluid tight connection with the cylinder 300 by packing rings 313 or the like.

As shown in Figure 16, the lower end member 302 is provided with a port 312 which allows of the admission of a portion of the natural" fluid to the cylinder 300. As the level of the fluid in the well rises above the circuit closer shown inFigure 16, the pressure naturally increases and fluid enters the to exert a pressure on the under si e of the pressure responsive piston 308. However, the prompt u ward movement of the piston 308 IS resiste by a coil spring 318 confined betwleen the piston 308 and the upper member 30 i The rompt upward movement of the piston 308 1s also resisted by means of an inward- 1y directed leaf spring 320 which extends in and engages a shoulder 322 on the lower end of a do 324.

As t e pressure on the under side of the piston 308 increases, the shoulder 322 on the dog 324 will ride over and snap by the leaf spring 320 so that the contacts 304 and 305 are brought into electrical engagement without arcin When the piston 308 is thus brought to the end of its u ward movement with somewhat of a snap, t e enlargement on the lower end of a retainer 330 Wlll be forcibly moved by an inwardly directed retaining spring 331 so that the piston is held in an GlGVfltGdlPO- sition. Of course, as long as the pressure remains on the under side of the piston 308, the contacts 304 and 305 will remain in effective electric contact, and even when the level of the fluid drops below the circuit closer shown in Figure 18, the pressure on the under side of the piston willremain for quite a while so that the pump or pumps, as the case may be, will remain in operation.

However, when the level of the fluid drops to a point below the inlet port of the lowermost pump, the pressure on the under side of the piston 308 will have decreased to such a point where the spring 318 will overcome the pressure and snap the piston to its lowermost position as shown in Figure 16. To do this the spring 318 must not only overcome the pressure ofthe fluid on the under side of the piston 308, but also must over- I come the spring 331. a housing 300, the ends 301 and 302 of WhlCh.

It is important to note that the size of the port 312 in the bottom of the circuit closer regulates the period of operation of the motors after the level of the fluid is dropped, as if the port is small it will effectively retard the descent of the piston. On the other hand, if the port 312 is of a comparatively large diameter, the piston will be allowed to descend more rapidly.

The switch shown in Figure 15 is placed at a level determined by the height to which the fluid rises naturally in the well.

\In summarizing the operation of the entire invention as disclosed, it is pointed out that the operation of the source of power within the casing 10 will set the combined fluid conductor and power transmitting shaft ort 312 55 in motion at a speed ranging from possibly 1800 to-3600 R. P. M.s and this will bring about the operation of the pump shown in Figure 1-.

By way of review, it will be seen that the invention includes a source of power and a fluid lift with a hydraulic motor between the source of power and the fluid lift to convert the rotary motion of the source of power into a reeiprocatory motion by which the fluid lift is operated, there being means in the form of a governor to neutralize the action of the hydraulic motor when the source of power is operating below a redetermined speed. It might be explained that the hydraulic motor between the source of power and the fluid lift consists of. the cylinder 58 and associated parts, the cylinder 140 and associated parts and the intervening motion transmitting and fluid distributing arrangement by which the rotationof the cylinder -58 and the concurrent reciprocation of the pistons therein will create a hydraulic power causing the reciprocation of the piston 96.

At this point it is again emphasized that the electric motor is submerged in the natural I products of the well and is enclosed within the rather thin casing so that the heat generated by the operation of the motor is effectively dissipated. This provides an oil cooled motor and permits the operation of the pump for long pumping periods.

The turning of the combined fluid conductor and power transmitting shaft results in the operation of the hydraulic pump so that an effective hydraulic pressure is set up and this is employed in the operation of the main piston 96.

As previously stated, the operation of the main piston results in the operation of the fluid lift. The fluid lifting pump may be either single or double acting.

With reference to the foregoing description taken in connection with the accompanying drawings, it will be seen that a pump constructed in accordance with this invention absolutely avoids the necessity of employing rods, cables,'shafts, and all other mechanical lifting equipment extending to the surface.

- As is well known, the rods employed in connection with present equipment frequently part or break under the strain of lifting the column of fluid and in addition to this the alternate carrying of the load first by the tubing and then by the rods results in the crystallization of these parts so that the same may at any time part or break under an excessive load.

Furthermore, the absence of rods greatly increases the fluid conducting capacity ofthe tubing and the number of possible strokes of the main pumping plunger or piston is greatly increasedr In fact, the pumping capacity of the apparatus is limited only by the size and capacity of the motor in use.

In the operation of the invention the timvalve with the hydraulic pump so that the fulldpressure of the hydraulic pump is uti- Having thus described the invention, what" is claimed is:

1. An apparatus of the character specified for use in wells consisting of a housing, a fluid lift located within said housing, a hy draulic puin connected to said fluid lift, said housing iieing adapted to contain a noncompressible fluid for use in connection with the hydraulic pump whereby the hydraulic pressure set up by the operation of said pump will operate the fluid lift, a power. unit having connection with said hydraulic pump, and means in the well to neutralize the action of the hydraulic pump during the" operation of the power unit below a pre-determined speed.

2. A pumping equipment for use in wells consisting of a'housing, a power unit located in the housing, a combined power transmit-' ting and fluid conducting hollow shaft arranged within the housing and connected to the power unit, a pump operatively connected to said power unit and adapted to create a hydraulic pressure, said housing being adapted to contain a non-compressible fluid to be acted on by said pump, and a fluid lift operated by the fluid ,set in motion by said pump, said shaft having a passage for said non-compressible fluid.

3. A pumping equipment for use in wells consisting of a housing, a source of power located within said housing, a combined fluid conducting and power transmitting hollow shaft having connection with said source of power, a hydraulic pump having connection with said shaft and adapted for creating a hydraulic pressure within the housing, said housing being adapted to containa nonco1npressible fluid to be acted on by said pump, a second combined fluid conducting and power transmitting hollow shaft connected to said pump, fluid. distributing means having connection with said second named shaft, and a pump operated by the fluid under pressure from said fluid distributing means.

4. A pumping equipment for use in wells consisting of a housing, a source of power arranged within the housing, a hydraulic pump operatively connected to the source of power, a combined fluid conducting and power transmitting hollow shaft connected to said hydraulic pump, a fluid distributing means associated with the combined fluid conducting and power transmitting hollow shaft and dividing the housing into high and low pressure chambers, a motor adapted to receive fluid under pressure from the high pressure reservoir, and a pump actuated by said motor and having means to elevate the products of a well.

5. A pumping equipment for use in wells consisting of a housing, a source of power within the housing, a hydraulic pump operatively connected to the source of power, a combined fluid conducting and power transmitting hollow shaft connected to said hydraulic pump, a fluid distributing means connected to the combined fluid conducting and power transmitting hollow shaft and dividing the housing mto high and low pressure reservoirs, the fluid distributing means being adapted to receive fluid under pressure from said combined fluid conducting and transmitting shaft, and a motor adapted to receive a fluid under ressure therefrom and a fluid lift connected to said motor and adapted for lifting the natural products of the well, the fluid in said housing being maintained separate from the natural products of the well.

' 6. A pumping equipment for use in wells consisting of a cylinder, means to supply a fluid under pressure to said cylinder, said cylinder being adapted to hold a fluid separate from the products of the well, a piston in said cylinder and having a rod, a second cylinder receiving said rod, a fluid lifting element in said second named cylinder and adapted for contact with the natural products ofthe well, said fluid lifting element having a gas pocket, and a sleeve receiving said piston rod and extending into said'gas pocket whereby admission of the natural products of the well to the sleeve is avoided, said rod having operative connection with said fluid lifting element.

7. A pumping equipment for use in wells.

consisting of a cylinder adapted to contain a fluid separate from the natural products of the well, a pumping barrel adjacent said cylinder, a piston in said cylinder and having a rod extending into said barrel, a pumping element in said barrel and having a longitudinal socket defining a gas trap, and a sleeve receiving said piston rod and extending into the gas trap, said rod having operative connection with said pumping element.

8. A pumping equipment for use in wells consisting of a housing, a source of power arranged within the housing, a combined fluid conducting and transmitting shaft arranged within the housing, a hydraulic pump operated by said combined fluid conducting and power transmitting shaft, a fluid acted on by said hydraulic pump, a second combined fluid conducting and power transmitting shaft connected to said hydraulic pump and adapted to receive fluid under pressure from the same, a fluid lift associated with said second named shaft, and means associated with said second named shaft for neutralizing the action of the pump when the source of power is operating below a predetermined speed, said means consisting of a governor carried by said second named shaft.

9. Ina fluid lift for use-in walls, a combined fluid conducting and power transmitting shaft having an outlet, a valve controllin said outlet, a centrifugal overnor contro ling said valve, and a flui distributin device connected to and driven by said sha v 10. A centrifugal governor for use in oil well pum s consisting of a combined power transmitting shaft and fluid conductor having an outlet, a valve casing associated with the outlet, a longitudinally movable valve for controlling the flow of fluid through said casing, and a fluid distributor connected to and operated by said shaft, a centrifugal governor mounted on the shaft and having a movable sleeve connected to said valve.

11. A pump for use in oil wells consisting of a housing having a reservoir, a fluid in said reservoir, a source of power arranged within the housing, a shaft connected to the "ing said actuating member, said pum being grogided with inlet and outlet means or said 12. A pump for use in wells consisting of a housing adapted to contain a fluid, means whereby the fluid in the housing is isolated from the products of the well, a source of power within the housing, a shaft connected to the source of power, a cylinder block mounted on and rotatable with the shaft, pistons movable within the block to place said fluid under pressure and having rods, a fixed cam, an actuating member operated by said cam and having connection with said rods, said actuating member being'rotatable with said block, and means operated by said fluid umlller pressure to raise the products of the we 13. The construction set forth in claim 12 and means in the well to neutralize the action of the piston when operating below a predetermined s eed.

14. A pump or the natural products of wells consistin of a housing, a hydraulicpump in the ousing, a fluid' distributing means associated with the hydraulic pump and adapted to receive fluid under pressure from the same, said fluid distributing means consisting of a valve and a valve casing, and a speed change mechanism located between and operatively connecting the hydraulic pump with the fluid distributin mechanism all of said mechanism being in longitudinal alignment. l

15. The construction set forth in claim 14, and means adjacent the hydraulic pump for operating the same.

16. In a fluid lift for use in wells, a combined fluid conducting and power transmitting shaft having a by-pass opening, a pressure fluid passing through said shaft, a fluid distributing device receiving said pressure fluid and having operative connection with and actuated by said shaft, a valve controlling said by-pass opening, and a governor controlling said valve, said governor having operative connection with and operated by said shaft; o

17. In a fluid lift for use in wells, a casing having high and low, pressure reservoirs, a fluid in said reservoirs, a pump for placing said fluid under pressure, a fluid distributing device controlling communication between said high and lower pressure reservoirs, a motion transmitting and fluid conducting shaft. having connection with and operated by said pump and having operative connection with said fluid distributing device to operate the same, said shaft being adapted to receive fluid from said pump and being provided with a by-pass opening, and a governor carried by said shaft and having a valve controlling said by-pass opening.

18. In a fluid lift for use in wells, a main pump having means for elevating the prodnets of a well, a motor having actuating connection with said pump, a source of power having operative-connection with said motor, and means in the well to neutralize the action of said motor when the source of poweir is operating below a predetermined s cc 19. In a fluid lift for use in wells, a housing, a source of power in the housing, a hydraulic motor in the housing, a combined fluid conducting and power transmittin shaft extending through the housing anc l operatively connecting the source of power and said hydraulic motor, said housing being adapted to contain a fluid for use with said hydraulic motor, means tending to main- I 

